CN101238310A - Continuously variable transmission - Google Patents
Continuously variable transmission Download PDFInfo
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- CN101238310A CN101238310A CNA2006800193101A CN200680019310A CN101238310A CN 101238310 A CN101238310 A CN 101238310A CN A2006800193101 A CNA2006800193101 A CN A2006800193101A CN 200680019310 A CN200680019310 A CN 200680019310A CN 101238310 A CN101238310 A CN 101238310A
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- 230000005540 biological transmission Effects 0.000 title abstract description 12
- 239000003607 modifier Substances 0.000 claims description 17
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- 230000001105 regulatory effect Effects 0.000 claims description 8
- 230000008676 import Effects 0.000 claims 1
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- 238000006243 chemical reaction Methods 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 230000007774 longterm Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 238000004904 shortening Methods 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
- F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
Abstract
In a continuously variable transmission ('CVT') using a toroidal-race continuously variable ratio device and a planetary gear mechanism, the rotation of the input shaft (12) is directly transmitted to the carrier C of the planetary gear mechanism (6<1>), and rotation resulting from gearing and reversal by the variator (5) is transmitted to the sun gear (S1). When the low clutch L is engaged, the rotation of the ring gear (R3) is transmitted via the reversing gear mechanism (7<1>) to the output shaft (13), and when the high clutch H is engaged, the rotation of the sun gear (S2) is transmitted to the output shaft (13).
Description
The present invention relates to stepless speed variator, it comprises continuous variable speed device (" transducer (variator) ") and the output gear ratio scope of the wide ranges that provides than the transducer by use planetary gear system and employing power cycle can be provided.More particularly, it relates to the stepless speed variator of a kind of input shaft and output shaft coaxial arrangement.
Stepless speed variator be proposed use ring translator and also wherein each element coaxial arrange (seeing WO03/100295A1).As showing that in Fig. 6 (a) lining described stepless speed variator 1 comprises: toroidal race; The rolling traction transducer 5 that comprises input disc 2, output disc 3 and roller 4, said roller are disposed between two discs and that can change them and radially contact positions two dishes; The planetary gear system 6 of band planet carrier C1, planet carrier C1 supports 3 small gear P1, P2, the P3 that arranges along axial space; The reverse gear device 7 of band planet carrier C2, planet carrier C2 supports 2 small gear P4, P5 that arrange along axially spaced-apart; Be included in the low break L that can stop sun gear S4 of reverse gear wheel apparatus outlet side and be inserted in the high/low state modifier 10 of the high clutch H between planetary second sun gear (height mode output gear) S2 and the output shaft 13.These assemblies are coaxial arrangement between input shaft 12 and output shaft 13.
Therefore, at low state, wherein low break L engages, high clutch H breaks away from, known to stepless speed variator 1 use planetary gear system 6 with associating planet carrier C1 (directly importing the rotation of input shaft 12) with in the rotation of the sun gear S1 of input side, described rotation via direct output planetary frame C1 and transducer 5 oppositely and adjust and outputs results to low mode output gear (the 3rd sun gear) S3.Planetary gear system 6 also makes the rotation reversing of described output gear S3 and outputs results to output shaft 13.
Should be appreciated that among Fig. 6 that shown, low/high state modifier 10 may also dispose the low clutch that is inserted between planet carrier C2 and the output shaft 13, and a similar above-mentioned high clutch H who is inserted between planetary pinion second sun gear S2 and the output shaft 13.
Known to stepless speed variator have big axial length also comprise 2 small gear P4, P5 spaced apart vertically because planetary gear system 6 comprises 3 small gear P1, P2 spaced apart vertically, P3 and counter gear mechanism 7.
The inventor of present patent application has invented a kind of stepless speed variator, and described speed changer uses dual planetary gear in the reverse gear device, and allows short axial distance.
According to first aspect of the present invention, stepless speed variator (CVT) comprises toroidal race continuous variable speed device (" transducer "), planetary gear system, reverse gear device and low/high state modifier, described transducer has rotation input and rotation output, the rotation input of transducer can be coupled to the input shaft of CVT drivingly, it is characterized in that:
Planetary gear system comprises two row planetary pinions and four internal coupling elements arranged, first element just, second element, three element, quaternary part.
So the drivable input shaft that is coupled to of first element is by described its rotation of input shaft decision; The drivable rotation output of being coupled to transducer of second element, thus its rotation of output speed decision of transducer passed through, and rotate oppositely rotating of direction by the CVT input shaft, and also transducer produces the rapid change of continuous variable.
At the low state of regulating by low/high state modifier, the drivable output shaft that is coupled to CVT of three element, three-element rotation relies on the counter-rotating of reverse gear device, and at the high state of regulating by low/high state modifier, the drivable output shaft that is coupled to CVT of quaternary part.
Because planetary gear system comprises 2 row/4 element type planetary pinions, so pinion shaft only needs short structure with at axially support two row small gears, and, the result, the bearing of the support two row small gears that rotate with free rotating manner also can have major diameter, and the bearing life ability is enhanced, in addition, the deflection of described pinion shaft is reduced, therefore reduce the subsidiary load fluctuation on the bearing, and the weight of small gear also becomes lighter, so centrifugal load reduces, and these can improve the precision and the long term maintenance highi degree of accuracy of pinion support together.
Same because system comprises two row planetary pinions, by axially shortening planetary gear system, stepless speed variator can be arranged compactly.
Preferably, planetary gear system is La Weina (Ravigneaux) type, is proved to be with practical value as 2 row/4 element type devices.Along with shortening in the axial direction, so stepless speed variator can be by compact layout, and its reliability has improved.
According to second aspect of the present invention, stepless speed variator (CVT) comprises toroidal race continuous variable speed device (" transducer "), planetary gear system, and the reverse gear device, low/the high state modifier, it is characterized in that:
Planetary gear system comprises the planet carrier that has first pinion shaft and second gear shaft, first sun gear, second sun gear, gear ring.
First pinion shaft supports first small gear and second small gear that rotates together, and second pinion shaft supports third pinion, first small gear or second small gear and third pinion engagement.
First small gear and the engagement of first sun gear, second small gear and the engagement of second sun gear, third pinion and gear ring engagement.
Planet carrier receives from input shaft and rotates input, and the output of the first sun gear receiving transducer is rotated, and described rotation causes producing via transducer the rotation reversing and the rapid change of output shaft.
At the low state of regulating by low/high state modifier, after relying on the reversing of reverse gear device, gear ring rotates and outputs to output shaft; And
At the high state of regulating by low/high state modifier, the rotation of second sun gear is output to output shaft.
Because the La Weina type planetary pinion known to planetary gear system comprises, and because first planet axis only needs support structure first small gear and second small gear of a weak point, and because gear ring is formed low state output gear, following influence on second pinion shaft is little, be designed to provide gear ratio to obtain stepless speed variator (CVT) function, and be accompanied by two kinds of low grades and overdrive direction at transducer, the power recirculation that adopts gear to switch, and can use and have large diameter relatively second pinion shaft.
The result, bearing at free rotation formula lower support first and second small gears also can have major diameter, and the bearing life ability improves, by using high rigidity, second small gear short, compact Layout, reduce the deflection of described axle, therefore reduce load fluctuation subsidiary on bearing, described in addition small gear weight also changes gently, centrifugal load reduces, and these can improve the precision and the energy long term maintenance pinpoint accuracy of pinion support together.
In addition, can be overlapping in the axial direction because under low state, form the gear ring of output gear and under high state, form second sun gear of output gear, following speed changer can closely be arranged by shortening planetary gear system in the axial direction.
Further, be coupled to planet carrier, and the output disc of transducer is coupled to first sun gear, can obtain compact simple connection by input shaft and input disc with transducer, therefore, from the central module of twin shaft configuration transducer.
Preferably, the reverse gear device comprises that band supports the dual planetary gear of the planet carrier of first small gear engage one another and second small gear, sun gear with first pinion, gear ring with above-mentioned second pinion, and the planet carrier and the sun gear of one of the gear ring of planetary gear system coupling or other reverse gear device, and, at low state, along with the gear ring braking, one of them rotation with another of planet carrier and sun gear is delivered to output shaft.
Therefore because the reverse gear device comprises dual planetary gear, following described reverse gear device can shorten in the axial direction, makes speed changer even compacter, and, especially, shorten in the axial direction.
Two input discs of transducer band preferably, an output disc or be positioned at the output disc of pairing back-to-back between the input disc, be clipped in the roller between input disc and the output disc, with two input discs, the input shaft of planetary gear system mentioned above and planet carrier are arranged to jointly support thrust, and first and second sun gears are supported by thrust-bearing planet carrier or input shaft with respect to integral arrangement on thrust direction too.
Thereupon, thrust by transducer and planetary gear system as a separate payment together support, and pinpoint accuracy support can long term maintenance, and the life-span of transducer can prolong, and the thrust that does not have essence is on element, for example the thrust-bearing of housing and housing.
Now will be by with reference to the accompanying drawings, only to describe certain embodiments of the present invention, wherein as the mode of example:
Fig. 1 is a schematic representation, has shown according to stepless speed variator structure of the present invention.
Fig. 2 is a speedometer, has shown (a) low state and high state (b).
Fig. 3 is a plotted curve, has shown the relation of transducer speed ratio and transmission gear ratio.
Fig. 4 is embodiment's schematic representation that the present invention partly revises.
Fig. 5 is a cross-sectional view, has shown the major component of the embodiment of the invention.
Fig. 6 is a schematic representation, has shown at (a) and the dissimilar prior art of part that (b) shows.
Fig. 7 is a schematic representation, has shown the technology of forming background of the present invention, and inventor of the present invention has made the present invention based on the above-mentioned background technology.
Fig. 8 is a speedometer, has shown (a) low state and (b) high state.
Fig. 9 is a cross-sectional view, has shown the major component of above-mentioned background technology.
In the stepless speed variator of describing in Fig. 71, the transducer 5 of annular is identical with description above with planetary gear system 6, but reverse gear device 7
1Comprise dual planetary gear.That is to say, planet carrier C0 supports small gear P4 and the P5 that engages one another, under free rotation mode, when other small gear P5 and gear ring R0 engagement, one of them small gear P4 and sun gear S0 engagement, the 3rd sun gear S3 (low mode output gear) of sun gear S0 and planetary gear system mentioned above 6 coupling in addition, gear ring R0 is fixed on the housing 15, and planet carrier C0 is coupled to output shaft 13 via low clutch L.
The speed changer 1 of Fig. 7
1Operation as showing in Fig. 8 speedometer.More particularly, as showing among Fig. 8 (a), (wherein low clutch L engages at low state, high clutch H separates), before being transferred to first sun gear (input gear) S1, the rotation of input shaft 12 (for example motor output rotate) is transferred to the planet carrier C1 of planetary gear system 6 by central shaft 12a, and is reversed by ring translator 5.When power passed through planetary gear system 6 recirculation, the rotation combination of the reverse gear of the rotation of the fixed speed of planet carrier C1 mentioned above and input gear S1 was from the 3rd sun gear S3 (output gear on low state limit) output result.
Here, because the relation between input side gear ratio (S1/P1) and the outlet side gear ratio (S3/P3), when transducer 5 overdrive (OD) time, output gear S3 rotates in oppositely (the sense of rotation of input shaft 12 as forward), and transducer 5 (UD, speed reduces side) change gear transmission from OD to low grade, therefore by 0 rotation (GN, the neutral gear that engages) point is in forward rotation.When transducer 5 farthest arrives the UD side, reach maximum forward rotation.
The transmission of rotation of described output gear S3 is to reverse gear device 7
1Input sun gear S0, its whole with it combination, and because gear ring R0 locking before gear ring C0 output, rotate oppositely.The rotation of described planet carrier C0 is via the low clutch L transmission that engages with output shaft 13.Therefore, at planet carrier C0 and output shaft 13, the backward rotation of output gear S3 becomes forward rotation.Yet, when speed changer 1 of the present invention
1When in automobile, using, speed changer 1
1The differential mechanism in transmission of power downstream side have in the middle of reversing device (not describing) again, and the forward rotation of output shaft mentioned above 13 becomes the output that is used for vehicle backing and rotates.That is to say that along with transducer 5 is shifted gears to UD from OD, output shaft (planet carrier C0) 13 rotates by GN point (zero rotates) and enters the rotation of advancing from reversing.
If low clutch L breaks away from, high clutch H engages, and system changes to high state.In this state, to output shaft 13, the rotation of the second sun gear S2 (height mode output gear) of planetary gear system 6 is not output with changing by high clutch H.As demonstration among Fig. 8 (b), the rotation of output shaft 12 directly is transferred to the planet carrier C1 of planetary gear system 6, and before being transferred to first sun gear (input gear) S1, by transducer 5 counter-rotatings.
By planetary gear system 6, the fixed speed forward rotation of planet carrier C1 mentioned above and the first sun gear S1 oppositely with hold the rotation combination that is connected, from second sun gear S2 output result, and here, input side gear ratio (S1/P1) and outlet side gear ratio (S2/P2) are approaching value or same values, in the maximum UD of the transducer of basis in the low mode mentioned above output speed of advancing in period, be switched to the direction that rotates backward a lot of after, the gear ratio of transducer 5 is formed output speed.In other words, when transducer 5 at maximum UD state the time, under height mode, second sun gear (output gear) S2 is in minimum advancement motion output speed in height mode, transducer 5 is changed connection from the UD side to the OD side, when doing like this, the progressive motion output speed improves.Should be appreciated that in automobile output period because reversing device again, the backward rotation side is corresponding to direction of forward movement.
Therefore, under low mode, when transducer 5 during at maximum OD state, speed changer 1 of the present invention
1Be in the top speed of operation backward, and, when speed changer 5 when the UD direction changes gear and connects, the forward direction running state is put and entered in system by geared neutral (GN), improve speed at the forward direction traffic direction, up to maximum UD point at transducer 5, be issued to the maximum output speed of forward movement at low state, system crosses and reaches high state at that point, therefore, along with transducer 5 in maximum UD position, system is in minimum output speed, roughly the same with the maximum output speed under low state mentioned above.Under height mode, when transducer 5 was transformed into the OD direction, forward direction operation output speed improved equally, and in the maximum OD position of transducer 5, reached the maximum output speed of forward direction operation.
By making transducer 5 be transformed into the UD direction by this way from OD, speed changer 1
1From operation conversion backward, the neutral gear by gear and enter the forward direction traffic direction, and by the conversion speed changer from the UD position to the OD direction, speed changer advance traffic direction continuously further raising speed up to reaching maximum output speed.
Fig. 9 has shown by the transmission types sectional view that schematically describes among Fig. 7, has planet carrier C1, and it is supported on axially straight three small gear P1, P2, P3; First sun gear (input gear) S1, itself and the first small gear P1 mesh; Second sun gear (height mode output gear) S2, itself and the second small gear P2 mesh; The 3rd sun gear (low mode output gear) S3, itself and third pinion P3 mesh.Planet carrier C1 has one of them the dish 2 carrier main-body 21a that form with transducer 5, and gear cap 21b and described main body become integral body.Carrier main-body 21a freely rotates via bearing 24 in speed changer case 22 upper supports.Further, described carrier main-body 21a and lid 21b have pinion shaft 23, and this pinion shaft supports integrally formed first, second and third pinion P1, P2 mentioned above, P3, forms freely via needle bearing 29 or lining and rotates.Should be appreciated that and also comprise lining when mentioning bearing.
The first sun gear S1 forms at hollow shaft 25 fore-ends, be coupled center output disc 3 (see figure 7)s of transducer 5 mentioned above of the foundation of described hollow shaft 25.The hollow space of described hollow shaft 25, rely on needle bearing or similar parts, input shaft (central shaft) 12 rotates supported freely, via shock absorber as its foundation, described input shaft 12 coupling engine output shafts (towards vehicle front), and connect at its fore-end (towards vehicle back side direction) spline with carrier main-body part 21a mentioned above.The second sun gear S2 forms on jack shaft 26,26 couplings of described jack shaft mentioned above low/the high clutch H of high state modifier (see figure 7).The 3rd sun gear S3 forms on quill 27, and described quill is freely rotated on jack shaft mentioned above, the be coupled sun gear S0 of reverse gear device mentioned above of described quill.
Because pinion shaft 23 mentioned above supports integrally formed straight in the axial direction three small gear P1, P2, P3, it has is microscler structure in the axial direction, and it is above described, owing to move maximum output speed and move the continuous gear shift of minimum output speed at the height mode forward direction probably consistent with the maximum UD of transducer 5 with the low mode forward direction, so the gear diameter of third pinion P3 reduces, so the diameter of pinion shaft 23 reduces equally.
The result, because the diameter of bearing 29 reduces equally and the life capacity of bearing 29 reduces, and pinion shaft 23 has the diameter that reduces, and will there be risk unfavourably in the validity of planet carrier C1 and life-span, load on the bearing increases simultaneously, and the result is because deflection takes place axle rigidity deficiency.
Same, the load aspect that is arranged in of planetary gear system 6 is inconvenient, centrifugal load for example, and three small gear P1, P2, P3 that integrally form are very heavy therein, and planet carrier C1 stands big centrifugal load.
Further, because three small gear P1, P2, the straight each other in the axial direction layout of P3, planetary gear system 6 is along axially being microscler, even and have a mind to shorten the length of reverse gear device, speed changer is in essence along axially still being microscler.
The speed changer that shows among Fig. 7 and Fig. 9 does not also have disclosed on the preference of the present invention date, this point is essential to be indicated.
Fig. 1 has shown the speed changer 1 that comprises in the present invention
2It comprises continuous changeable device (" transducer ") 5, planetary gear system 6
1, reverse gear device 7
1, low/high-transformation device 10.Transducer 5 is rolling traction devices of an annular, and it comprises two input discs 2 and 2 that are coupled to input shaft 12, is coupled to the independent output disc 3 of hollow shaft 25, and powered rollers 4 and 4 is clipped between two dishes.Input disc 2 and output disc 3 have the arc hole 2a and the 3a of the formation circle that falls in, and under this method, they face with each other and form a two-chamber and be clipped between two row powered rollers 4 and 4.Therefore they form the layout of compensating for each other with input disc thrust.Tilt by the direction conversion at vertical their axles, powered rollers 4 and 4 can be shifted gears continuously, therefore changes the radius that contacts with output disc 3 with input disc 2.Transducer 5 speed ratios of the present invention (output speed/input speed) from-0.4 to 2.5.Should be appreciated that because output disc 3 with respect to input disc 2 backward rotation, so speed ratio is "-" (bearing).
Be coupled to first sun gear (second element) S1 of the output disc 3 of transducer 5, with first small gear P1 engagement, the described first sun gear S1 forms the input gear that is used for from transducer 5 input gears rotations.The second small gear P2 and third pinion P3 engage one another, be arranged on the same plane (to overlap each other in the axial direction), and in the time of third pinion P3 and gear ring R3 engagement, the second small gear P2 and second sun gear S2 engagement.By the high clutch of low/high state modifier 10, second sun gear (quaternary part) S2 is coupled to output shaft 13, so form the height mode output gear.Gear ring (three element) R3 is coupled to reverse gear device 7
1Planet carrier C0, therefore form the low mode output gear.
Should be appreciated that a kind of layout that alternatively adopts, in this arrangement, third pinion P3 and first small gear P1 engagement, dual planetary gear and sun gear S1 are arranged in the same side (towards transducer).
Reverse gear device 7
1Comprise dual planetary gear, this gear has two intermeshing small gears (the first small gear P4 and the second small gear P5), describes in as mentioned, and wherein planet carrier C0 is coupled to gear ring R3, and gear ring R0 is fixed on the housing 22, and sun gear S0 is coupled to output shaft 13 by roller clutch L.
Stepless speed variator of the present invention (CVT) 12 operates in Fig. 2 mode that shows in the table of shifting gears.Be to be understood that, although the speedometer of Fig. 2 shows that the first and second small gear P1, P2 are as a common spool gear, gear ratio S1/P1 is identical with S2/P2, and output speed and transducer output line are overlapping, gear ratio mentioned above (S1/P1) and (S2/P2) may be changed, therefore not overlapping at the output speed and the transducer output line of the demonstration of Fig. 8 speedometer, this does not mention and can take place.Should be appreciated that moment of torsion is assigned with at the gear ratio that helps transmission efficiency of comparing with transducer, and can improve and make as a whole transmission efficiency by changing gear ratio S1/P1 and S2/P2.Further, just in case gear ratio mentioned above is identical, by the speed of raising output gear under height mode, and use higher gear ratio in speed changer as a whole, fuel can be modified in the high-speed region burning.
As showing among Fig. 2 (a), under low state (wherein low clutch L engages, and high clutch H breaks away from), the rotation of being coupled to the input shaft 12 of engine output shaft directly is transferred to planetary gear system 6
1Planet carrier C, and via the gear rotation result transmission of transducer 5 after oppositely to first sun gear (input gear) S1.Along with power recirculation, by planetary gear system, the fixed speed of planet carrier mentioned above rotates and the gear of first sun gear rotates (transducer gear ratio) combination, and the result outputs to the gear ring R3 as low state output gear.Should be appreciated that during this time, because high clutch H breaks away from, second sun gear R2 idle running.Here, along with speed changer 5 from the OD side UD side of transferring the files, output gear R3 is (GN point) from the backward rotation to the neutral, in this position output speed 0, moment of torsion unrestrictedly scatters and disappears, further change gear to the OD side, this raising speed is to positive turn side (direction same with the rotation of output shaft).
Same, the rotation of described output gear R3 directly is transferred to reverse gear device 7
1Planet carrier C0, and owing to gear ring R0 stops to reverse and exports from sun gear S0.In this manner, the rotation counter-rotating of output gear R3 mentioned above and planet carrier C0, and the output of the backward rotation of output gear R3 is as the operation output speed backward of sun gear S0, and the output of the forward rotation of output gear R3 is as the forward direction operation output speed of sun gear S0.
If low clutch L breaks away from, high clutch H engages, and then system is transformed into high state.In this state, the rotation of output shaft 12 directly outputs to planetary gear system 6
1Planet carrier C, and rotate result transmission to the first sun gear S1 by transducer 5 gear after oppositely, and these are by described planetary gear system 6
1Combined.The result is exported from the second sun gear S2 as the high state output gear.Should be appreciated that during this time, because low regime clutch L breaks away from sun gear S0 and reverse gear device 7
1Planet carrier C0 idle running, and therefore planetary gear system 6
1Gear ring R3 dally equally.Further, because gear ratio S1/P1 is identical with S2/P2, second sun gear S2 output mentioned above is rotated (transducer gear ratio) identical rotation with the gear output from transducer 5, and because the connection of high clutch H, described transducer gear ratio is as the high state forward direction operation output speed output from output shaft 13.
For preamble being described with reference to the chart among the figure 3, under low state, when the speed ratio (output speed/input several times) of transducer 5 when OD holds (probably-2.5), stepless speed variator (IVT) 1
2Rotate under the turn direction with predetermined speed ratio (general 0.25), and when the continuous change gear of transducer 5 during to the UD side, the speed ratio of stepless speed variator 12 mentioned above reduces continuously, and stepless speed variator 1
2Approaching-0.8 place of the speed ratio of speed ratio in transducer 5 be 0, this place is for geared neutral (GN point).Same, when transducer 5 when the UD direction continuously changes gear, the speed ratio of stepless speed variator 12 improves continuously in the backward rotation direction, and when transducer 5 reaches UD end (probably-0.4), stepless speed variator 1
2Speed ratio probably is-0.5.
Now, in this state, system is transformed into high state.At high state, when the speed ratio of transducer 5 during at UD end mentioned above, the speed ratio of stepless speed variator 12 is the value identical with low mode mentioned above (probably being-0.5), and here, if the speed ratio of transducer 5 changes in the OD direction continuously from UD end mentioned above, stepless speed variator 1 so
2Speed ratio from low state mentioned above continuously the back improving to sense of rotation.In the raising of back on sense of rotation, when continuing when the OD direction changes the gear of transducer 5, the speed ratio of transducer 5 reaches OD end (general-2.5), stepless speed variator 1 as for described speed
2Speed ratio probably-2.75, this is a slowest ratio.
Should be appreciated that in table mentioned above the sense of rotation of input shaft 12 (being exactly the sense of rotation of motor) is used as the formation forward rotation, speed ratio is expressed as " just ", and therefore, because because its circular pattern is rotated on oppositely, the speed ratio of transducer 5 is " bearing ".Because stepless speed variator of the present invention (CVT) 1
2In automobile, use, because reverse gear in differential mechanism, rotates oppositely again, thereupon work as speed changer 1
2Speed ratio when being " just ", the vehicle operating direction backward, and when described speed ratio be " bearing ", the vehicle operating direction is forward.Therefore, under low state, the gear of transducer 5 can be from CD end to the UD conversion, and therefore when vehicle during from inverted running, car speed improves gradually, by neutral gear (GN), enter the forward direction operation, in addition, be transformed into high state at the UD of transducer 5 end system, and transducer 5 is changed to the OD direction from UD, so car speed improves at the forward direction traffic direction continuously.
Fig. 4 has shown the improved train of gearings of part, and wherein the reverse gear device 7
2Comprise dual planetary gear similarly, but gear ring R0 is coupled to low break L, and planet carrier C0 is directly coupled to output shaft 13.And planetary gear system 6
1The sun gear S0 of low state output gear R3 coupling reverse gear device 72, high clutch H assigns between planetary high state output gear S0 and the output shaft 13.
The mode of operation of present embodiment is identical with Fig. 2 description, except the position the same with the low state output gear R3 in Fig. 2 (a) lining is sun gear S0.More particularly, under low state, the rotation of output gear R3 is imported into reverse gear device 7
2Sun gear S0, and be inverted by fixed gear ring R0, and output to output shaft 13 from planet carrier C0 by engaging low break L.At described reverse gear device 7
1With 7
2In, input and output power may comprise and not be that sun gear S0 is exactly planet carrier C0 that these are useless superfluous words.
Fig. 5 is a cross-sectional view, has shown according to planetary pinion of the present invention.Planetary gear system 6
1Be the La Weina type, comprise 2 row of forming by simple planetary pinion 31 and dual planetary gear 32.Described planetary gear system 6
1Have the planet carrier C that supports the first small gear P1, the second small gear P2 and third pinion P3; First sun gear (input gear) S1 with first pinion; Second sun gear (height mode output gear) S2 with second pinion; Low mode output gear R3 with the third pinion engagement.Planet carrier C comprises carrier main-body 33 and planet carrier lid 35, described lid integrally is connected with described main body, and carrier main-body 33 supports freely via the bearing on speed changer case 22 24 and rotates, be coupled to the output disc 2 of one of them transducer 5 simultaneously, be fastened on the input shaft 12 with the spline connection and by a nut 34 in addition, described input shaft 12 extends to the center of transducer 5.
The second short and small gear shaft 37 that uses with total first pinion shaft 36 of above-mentioned simple dual planetary gear 31,32 and double pinion 32 is provided, and is prevented from rotation and crosses carrier main-body 33 mentioned above and carrier cover 35.When third pinion P3 was supported on second pinion shaft 37, the first small gear P1 and the second small gear P2 were axial adjacent one another are being supported on first pinion shaft 36.The formation of the first small gear P1 and the second small gear P2 integral body, and.Need the same number of teeth although they are unnecessary, but they have the same number of teeth in embodiments of the invention, and public small gear P1 and P2 are supported on first pinion shaft mentioned above, 36 cofree rotations via needle bearing 37 and 37 (or lining).Third pinion P3 is supported on second pinion shaft 37 mentioned above via needle bearing 39 (or lining) and freely rotates.
The first sun gear S1 mentioned above forms at hollow shaft 25 fore-ends, and described hollow shaft 25 is supported on the input shaft 12 and freely rotates.At its rear end part, it is coupled to the output disc 3 of transducer 5.The second sun gear S2 forms at the back segment of jack shaft 26, and described jack shaft 26 supports to do freely on the cardinal extremity part that is installed in input shaft 12 and rotate, and at its front end (backward), it is connected with the high clutch H of low/high state modifier 10.Output gear R3 can not be broken away from but via annular spline assembly 41, is fixed on reverse gear device 7
1Carrier flange on.
Same, each thrust-bearing 42 and 43 is arranged between the leading flank and trailing flank of spline coupling unit 33a of carrier main-body 33 mentioned above, between the front-end face of the ear end face of hollow shaft 25 and jack shaft 26, and thrust-bearing 45 is arranged in the ear end face and the reverse gear device 7 of the jack shaft 26 that the second sun gear S2 is formed
1Between the front end of sun gear S0.By this way, with reference to hollow shaft 25 that has the first sun gear S1 and the jack shaft 26 that has the second sun gear S2, compensate for mutually by meshing sun gear S1 that the first and second small gear P1 and P2 produce and the thrust of S2 respectively, and, because the whole carrier main-body 33 that is connected with input shaft 12, they are by equally with in planetary gear system 6
1In approaching mode support.Should be appreciated that input shaft 12 and and its integrally formed planet carrier modes of being created in the transducer 5 two thrusts between the dish 2 and 2 with setoff support transducer 5 and planetary gear system 6
1The supporting structure that has relative force direction closure is as single-row.Be to be understood that, thrust-bearing 43 may not need, in this case, the reasoning that acts on the direction left in the drawings on the second sun gear S2 acts on the second sun gear S2 by jack shaft 25 with snap ring 48 and thrust-bearing 49, and the thrust of first sun gear and described planet carrier C setoff.
If first pinion shaft 36 mentioned above supports two small gear P1 and P2, it will comprise a kind of structure (comparing with the step pinion that shows among Fig. 7) of enough weak points, and low state output gear will comprise gear ring R3, therefore for obtaining stepless speed variator 1
2Function has some restrictions on gear ratio, and first pinion shaft 36 can be the parts with big axial diameter.Therefore, bearing 37 can have big diameter, and life capacity can be enhanced, the rigidity of other first pinion shaft 36 can be enhanced, because the deflection of axle can be lowered, small gear weight becomes lighter, and centrifugal load reduces, and these can keep long-term support small gear P1 and the validity of P2 together.
Further, because act on and the first and second small gear P1 and first and second sun gear S1 of P2 engagement and the thrust on the S2, meshing planetary gear device 6
1Be supported for and transducer 5 system as a whole, following since with the integral arrangement of the transducer output disc 2 of output shaft 12 and planet carrier C, with in the stepless speed variator 12 that closed support combines the thrust load reduction of 22 li of housings.
Further, planetary gear system 6
1Can use gear ring R3 as low state output gear, therefore low state and high state output gear R3 and S2 can be at axial overlaps, and axial length can shorten.
Claims (5)
1. a stepless speed variator (" CVT "), comprise toroidal race continuously variable ratio equipment (" transducer "), planetary gear system, reverse gear device and low/high state modifier, described transducer has to rotate imports and rotates output, the rotation input of transducer can be coupled to the CVT input shaft drivingly, it is characterized in that:
Planetary gear system comprises two row planetary pinions, and has four coupled outside elements, i.e. first element, second element, three element and quaternary part,
First element can be coupled to input shaft drivingly, so by described its rotation of output shaft decision; Second element can be coupled to the rotation output of transducer drivingly, so its rotation of output speed decision by transducer and is rotated oppositely rotating of direction by the CVT input shaft, and transducer produces continuous variable velocity and change,
At the low state of regulating by low/high state modifier, three element can be coupled to the output shaft of CVT drivingly, three-element rotation relies on the counter-rotating of reverse gear device, and at the high state of regulating by low/high state modifier, the quaternary part can be coupled to the output shaft of CVT drivingly.
2. stepless speed variator as claimed in claim 1, wherein, planetary gear system is the La Weina type.
3. a stepless speed variator (" CVT ") comprises toroidal race continuously variable ratio equipment (" transducer "), planetary gear system, and reverse gear device and low/high state modifier is characterized in that:
Planetary gear system has planet carrier, first sun gear, second sun gear and gear ring, and this planet carrier has first pinion shaft and second pinion shaft,
First pinion shaft supports first small gear and second small gear that rotates together, and second pinion shaft supports third pinion, and first small gear or second small gear and third pinion engagement,
First small gear and the engagement of first sun gear, second small gear and the engagement of second sun gear, third pinion and gear ring engagement,
Planet carrier receives from input shaft and rotates input, and first sun gear receiving transducer output rotation, and described rotation is to rotate oppositely and the result of rapid change by the input shaft that transducer produces,
At the low state of regulating by low/high state modifier, after relying on the counter-rotating of reverse gear device, the rotation of above-mentioned gear ring outputs to output shaft,
At the high state of regulating by low/high state modifier, the rotation of second sun gear outputs to output shaft.
4. stepless speed variator as claimed in claim 3, wherein the reverse gear device comprises the dual planetary gear that has the planet carrier that supports first and second small gears be engaged with each other, mesh the sun gear of first small gear and mesh the gear ring of above-mentioned second small gear,
The gear ring of planetary gear system is coupled in the planet carrier of reverse gear device and the sun gear one or another, and under low state, along with the gear ring braking, one of them transmits another the output shaft that turns to planet carrier and sun gear.
5. as any described stepless speed variator in the claim 1 to 4, wherein said transducer has two input discs, and output disc or a pair of back-to-back output disc that is positioned between the input disc are clipped in the roller between input disc and the output disc; The planet carrier of two input discs, input shaft and above line star gear devices is arranged common bearing thrust, and via thrust-bearing, first and second sun gears are supported with respect to the planet carrier or the input shaft of one layout in thrust direction equally.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP104319/2005 | 2005-03-31 | ||
| JP2005104319A JP4637632B2 (en) | 2005-03-31 | 2005-03-31 | Continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101238310A true CN101238310A (en) | 2008-08-06 |
Family
ID=36500895
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2006800193101A Pending CN101238310A (en) | 2005-03-31 | 2006-03-31 | Continuously variable transmission |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US8142323B2 (en) |
| JP (1) | JP4637632B2 (en) |
| CN (1) | CN101238310A (en) |
| DE (1) | DE112006000791T5 (en) |
| GB (1) | GB2440058A (en) |
| WO (1) | WO2006103294A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7011600B2 (en) | 2003-02-28 | 2006-03-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
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| EP1811202A1 (en) | 2005-12-30 | 2007-07-25 | Fallbrook Technologies, Inc. | A continuously variable gear transmission |
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| US8230961B2 (en) * | 2009-11-04 | 2012-07-31 | Toyota Motor Engineering & Manufacturing North America, Inc. | Energy recovery systems for vehicles and wheels comprising the same |
| US8172022B2 (en) * | 2009-11-30 | 2012-05-08 | Toyota Motor Engineering & Manufacturing North America, Inc. | Energy recovery systems for vehicles and vehicle wheels comprising the same |
| US8578802B2 (en) | 2009-12-16 | 2013-11-12 | Allison Transmission, Inc. | System and method for multiplexing gear engagement control and providing fault protection in a toroidal traction drive automatic transmission |
| KR20120094060A (en) | 2009-12-16 | 2012-08-23 | 알리손 트랜스미션, 인크. | Variator fault detection system |
| EP2513514A4 (en) * | 2009-12-16 | 2013-08-07 | Allison Transm Inc | System and method for controlling endload force of a variator |
| CA2784373C (en) | 2009-12-16 | 2017-11-07 | Allison Transmission, Inc. | Fast valve actuation system for an automatic transmission |
| US8401752B2 (en) * | 2009-12-16 | 2013-03-19 | Allison Transmission, Inc. | Fail-to-neutral system and method for a toroidal traction drive automatic transmission |
| CN105179672B (en) * | 2009-12-16 | 2017-07-11 | 艾里逊变速箱公司 | The control loop of converter micro-tensioning system control method and converter |
| BR112012021711B1 (en) * | 2010-02-23 | 2020-12-08 | Nissan Motor Co., Ltd. | control device for a continuously variable transmission for a vehicle |
| US8512195B2 (en) | 2010-03-03 | 2013-08-20 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
| KR20130131314A (en) | 2010-08-16 | 2013-12-03 | 알리손 트랜스미션, 인크. | Gear scheme for infinitely variable transmission |
| US8888643B2 (en) | 2010-11-10 | 2014-11-18 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| EP2655938A4 (en) | 2010-12-15 | 2016-07-27 | Allison Transm Inc | Variator switching valve scheme for a torroidal traction drive transmission |
| CA2821743C (en) | 2010-12-15 | 2018-09-11 | Allison Transmission, Inc. | Dual pump regulator system for a motor vehicle transmission |
| CN103370562B (en) | 2010-12-15 | 2016-03-23 | 艾里逊变速箱公司 | For controlling to equipment and the method for the fluid stream of gear in automatic transmission |
| AU2012240435B2 (en) | 2011-04-04 | 2016-04-28 | Fallbrook Intellectual Property Company Llc | Auxiliary power unit having a continuously variable transmission |
| WO2012145838A1 (en) * | 2011-04-29 | 2012-11-01 | Transmission Cvtcorp Inc. | Drivetrain provided with a cvt |
| WO2013109723A1 (en) | 2012-01-19 | 2013-07-25 | Dana Limited | Tilting ball variator continuously variable transmission torque vectoring device |
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| US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
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| US9353842B2 (en) * | 2012-09-07 | 2016-05-31 | Dana Limited | Ball type CVT with powersplit paths |
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| US9638296B2 (en) | 2012-09-07 | 2017-05-02 | Dana Limited | Ball type CVT including a direct drive mode |
| WO2014078583A1 (en) | 2012-11-17 | 2014-05-22 | Dana Limited | Continuously variable transmission |
| WO2014124063A1 (en) | 2013-02-08 | 2014-08-14 | Microsoft Corporation | Pervasive service providing device-specific updates |
| JP2016512312A (en) | 2013-03-14 | 2016-04-25 | デーナ リミテッド | Ball-type continuously variable transmission |
| WO2014159756A2 (en) | 2013-03-14 | 2014-10-02 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variatory drive |
| WO2014172422A1 (en) | 2013-04-19 | 2014-10-23 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| WO2014197711A1 (en) | 2013-06-06 | 2014-12-11 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
| US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
| WO2015073883A1 (en) | 2013-11-18 | 2015-05-21 | Dana Limited | Infinite variable transmission with planetary gear set |
| US9644724B2 (en) | 2014-10-17 | 2017-05-09 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
| US9651127B2 (en) | 2014-10-17 | 2017-05-16 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low part count |
| US9644721B2 (en) | 2014-10-17 | 2017-05-09 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges and low variator load at vehicle launch |
| US9382988B2 (en) * | 2014-10-17 | 2016-07-05 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
| US9512911B2 (en) | 2014-10-17 | 2016-12-06 | Allison Transmission, Inc. | Split power continuously variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
| US9772017B2 (en) | 2014-10-17 | 2017-09-26 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low variator loading at vehicle launch |
| US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
| US10047861B2 (en) | 2016-01-15 | 2018-08-14 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
| TW201825805A (en) | 2016-03-18 | 2018-07-16 | 福柏克智慧財產有限責任公司 | Stator and stator assembly for continuously variable transmission and method for controlling continuously variable transmission |
| US10023266B2 (en) | 2016-05-11 | 2018-07-17 | Fallbrook Intellectual Property Company Llc | Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmissions |
| JP6583347B2 (en) * | 2017-05-19 | 2019-10-02 | トヨタ自動車株式会社 | Gear transmission |
| US11215268B2 (en) | 2018-11-06 | 2022-01-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
| WO2020176392A1 (en) | 2019-02-26 | 2020-09-03 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5607372A (en) | 1995-01-13 | 1997-03-04 | The Torax Company, Inc. | Co-axial drive for a toroidal drive type transmission |
| JP4062809B2 (en) * | 1999-02-03 | 2008-03-19 | 日本精工株式会社 | Continuously variable transmission |
| US6059685A (en) * | 1999-05-06 | 2000-05-09 | Ford Global Technologies, Inc. | Coaxial traction drive automatic transmission for automotive vehicles |
| DE10021912A1 (en) | 2000-05-05 | 2001-11-08 | Daimler Chrysler Ag | Drive train for motor vehicle has second planet wheel with diameter such that for stepping up of variable speed gear contact point of second planet wheel with driven element corresponds to center of rotation of second planet wheel |
| DE10040039A1 (en) | 2000-08-11 | 2002-02-21 | Daimler Chrysler Ag | Change gear assembly |
| DE10039779A1 (en) * | 2000-08-16 | 2002-02-28 | Daimler Chrysler Ag | Gear shift device has second transmission member of final transmission locked in lower driving range at low speeds |
| DE10121042C1 (en) * | 2001-04-28 | 2003-05-08 | Daimler Chrysler Ag | Change gear arrangement with a toroidal continuously variable transmission and a planetary gear total gear |
| DE10132674A1 (en) | 2001-07-05 | 2003-01-16 | Daimler Chrysler Ag | Change gear arrangement with a toroidal continuously variable transmission and a summation gear planetary gear type |
| JP2003176862A (en) * | 2001-12-11 | 2003-06-27 | Jatco Ltd | Power transmission device |
| GB2384835B (en) * | 2002-02-01 | 2006-02-22 | Torotrak Dev Ltd | Continuously variable transmission system |
| CN1656329B (en) | 2002-05-28 | 2010-05-05 | 托罗特拉克(开发)有限公司 | Continuously variable ratio transmission system |
| DE10249484A1 (en) * | 2002-10-24 | 2004-05-06 | Zf Friedrichshafen Ag | Dual area transmission unit with branched output, comprising two minus planetary gear sets and friction wheel alterator designed as single line device |
| GB2418235A (en) | 2004-09-20 | 2006-03-22 | Torotrak Dev Ltd | CVT with a compact variator which transmits less than 100% of engine power |
-
2005
- 2005-03-31 JP JP2005104319A patent/JP4637632B2/en active Active
-
2006
- 2006-03-31 CN CNA2006800193101A patent/CN101238310A/en active Pending
- 2006-03-31 WO PCT/EP2006/061254 patent/WO2006103294A1/en active Application Filing
- 2006-03-31 DE DE112006000791T patent/DE112006000791T5/en not_active Withdrawn
- 2006-03-31 US US11/910,450 patent/US8142323B2/en active Active
-
2007
- 2007-09-26 GB GB0718789A patent/GB2440058A/en not_active Withdrawn
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| CN102374016A (en) * | 2010-07-22 | 2012-03-14 | 福特全球技术公司 | Accessory drive and engine restarting system |
| CN103133613A (en) * | 2011-11-21 | 2013-06-05 | 通用汽车环球科技运作有限责任公司 | Two-mode continuously variable transmission |
| CN103133613B (en) * | 2011-11-21 | 2017-03-01 | 通用汽车环球科技运作有限责任公司 | Double mode buncher |
| CN103244625B (en) * | 2012-02-10 | 2016-09-14 | 通用汽车环球科技运作有限责任公司 | Compound planetary front-wheel drive buncher |
| CN103244625A (en) * | 2012-02-10 | 2013-08-14 | 通用汽车环球科技运作有限责任公司 | Compound planetary front wheel drive continuously variable transmission |
| CN103573953A (en) * | 2012-07-31 | 2014-02-12 | 通用汽车环球科技运作有限责任公司 | Simple planetary gearset continuously variable transmission |
| CN105257820A (en) * | 2014-07-08 | 2016-01-20 | 本田技研工业株式会社 | Continuously variable transmission for vehicle |
| CN105257820B (en) * | 2014-07-08 | 2017-07-04 | 本田技研工业株式会社 | Infinitely variable speed device for vehicles |
| CN107002843A (en) * | 2014-12-16 | 2017-08-01 | 本田技研工业株式会社 | Buncher |
| CN107002843B (en) * | 2014-12-16 | 2019-06-25 | 本田技研工业株式会社 | Stepless transmission |
| CN107013652A (en) * | 2016-01-28 | 2017-08-04 | 铃木株式会社 | Stepless speed change device |
| CN107013653A (en) * | 2016-01-28 | 2017-08-04 | 铃木株式会社 | Stepless speed change device |
| CN107013652B (en) * | 2016-01-28 | 2019-04-19 | 铃木株式会社 | Stepless speed change device |
| CN107013653B (en) * | 2016-01-28 | 2019-04-19 | 铃木株式会社 | Stepless speed change device |
| CN108368922A (en) * | 2016-11-23 | 2018-08-03 | 艾斯特拜克有限公司 | Contiuously variable transmission |
| CN110043620A (en) * | 2018-01-15 | 2019-07-23 | 怀化沃普环保科技有限公司 | Planetary gear and the fixed Contiuum type planetary transmission of axis |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2006283871A (en) | 2006-10-19 |
| WO2006103294A1 (en) | 2006-10-05 |
| US20090048054A1 (en) | 2009-02-19 |
| GB0718789D0 (en) | 2007-11-07 |
| DE112006000791T5 (en) | 2008-02-07 |
| GB2440058A (en) | 2008-01-16 |
| US8142323B2 (en) | 2012-03-27 |
| JP4637632B2 (en) | 2011-02-23 |
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